EP1767810B1 - Dispositf de valve d'amortisseur ayant une évolution progressive de la force d'amortissement - Google Patents

Dispositf de valve d'amortisseur ayant une évolution progressive de la force d'amortissement Download PDF

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Publication number
EP1767810B1
EP1767810B1 EP06017716A EP06017716A EP1767810B1 EP 1767810 B1 EP1767810 B1 EP 1767810B1 EP 06017716 A EP06017716 A EP 06017716A EP 06017716 A EP06017716 A EP 06017716A EP 1767810 B1 EP1767810 B1 EP 1767810B1
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EP
European Patent Office
Prior art keywords
valve
disc
vibration damper
blow
resilient
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP06017716A
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German (de)
English (en)
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EP1767810A3 (fr
EP1767810A2 (fr
Inventor
Klaus Dipl.-Ing. Schmidt
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ThyssenKrupp Bilstein Suspension GmbH
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ThyssenKrupp Bilstein Suspension GmbH
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Publication of EP1767810A3 publication Critical patent/EP1767810A3/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/34—Special valve constructions; Shape or construction of throttling passages
    • F16F9/348—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body
    • F16F9/3484—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body characterised by features of the annular discs per se, singularly or in combination
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
    • F16F9/512—Means responsive to load action, i.e. static load on the damper or dynamic fluid pressure changes in the damper, e.g. due to changes in velocity

Definitions

  • the invention relates to a hydraulic vibration damper according to the preamble of patent claim 1.
  • Such a vibration damper is from the DE 10 2004 050 732 A1 known.
  • the increasing damping force ensures that the damper speed is reduced before reaching the end stops in order to reduce the impact forces. With this striking would namely both mechanical wear or deformation and unwanted noise during driving connected.
  • a Dämpfventil comprising a first damping valve, which merges in a first operating range with increasing flow rate of a damping medium in a passage operating position, wherein a second operating range is influenced with a progressive damping force characteristic of a throttle body in conjunction with a spool, which is convertible to a closed position ,
  • the spool has a pressurized surface which, depending on the flow velocity of the Damping medium acts in the closing direction on the spool.
  • a separate spool is necessary in addition to the damping valves of the working piston or the bottom valve.
  • This separate spool acts either with the body of the working piston or with the body of the bottom valve and forms with this a throttle point.
  • the flow cross section of this throttle point decreases with increasing working piston speed, so that the damping force of the vibration damper increases progressively. If a certain critical value of the flow cross-section of the throttle point is reached, the pressure in the vibration damper rises to a critical value, when it reaches a pressure relief valve, which has a so-called blow-off function opens, so that the progressive damping force increase is canceled and the Damping force does not increase further, but remains at the achieved high level.
  • a disadvantage of this known vibration damper is that the structural design of the valve device is complex due to the required separate valve spool and therefore is also associated with relatively high costs.
  • the separate valve spool requires a relatively large axial height for the valve device.
  • the invention has for its object to provide a vibration damper according to the preamble of claim 1, which is structurally simple and in which the progressive Dämpfkraftverlauf effecting valve device has a low axial height.
  • variable throttle point the flow cross section for the damping medium as the working piston speed increases reduces and thus provides for the progressive increase of the Dämpfkraftverlaufes, formed directly between the damping force during normal operation determining valve disc on the one hand and cooperating with this valve disc annular disc on the other.
  • the pressure-limiting valve having a blow-off function has, according to the invention, an annular disk assigned to the valve disk of the damping valve, which in turn has a surface facing the valve disk. This surface forms with the valve disc from a variable throttle point, which ensures at high working piston speeds from about 2 m / sec for a progressive increase in the damping force curve of the vibration.
  • a variable throttle point which ensures at high working piston speeds from about 2 m / sec for a progressive increase in the damping force curve of the vibration.
  • valve device according to the invention with which the variable throttle point is formed, may be formed on the working piston of the vibration damper. If it is a vibration damper with bottom valve, the two-chamber principle of action works, so the valve device according to the invention can be provided either only on the working piston or only on the bottom valve or both the working piston and the bottom valve.
  • valve device according to the invention can be advantageously designed as an effective only in the compression stage of the vibration damper valve device. However, it is also conceivable to provide the valve device according to the invention as effective only in the rebound of the vibration damper valve device. Furthermore, it is also conceivable that the valve device according to the invention is effective in both directions of movement of the working piston (ie both in the tension and in the pressure stage).
  • the blow-off valve may be formed as a spring-loaded pressure relief valve.
  • the blow-off valve comprises a cylindrical shell having a radial shoulder disposed on its inner wall and extending inwardly, i. extends towards the center of the vibration damper. This paragraph forms an abutment for the annular disc, which forms the variable throttle with the valve disc.
  • a spring washer is arranged, which biases the pressure relief valve in the closing direction with a predetermined spring force.
  • the preload with which this spring washer is installed inside the jacket of the pressure relief valve, allows the pressure at which the pressure relief valve opens to achieve the blow-off effect.
  • the spring washer can of course also be provided a coil spring or a combination of spring washer and coil spring.
  • the invention makes use of the knowledge that the opening movement of the valve disc, which in normal operation of the vibration damper its damping characteristic determined, can be exploited to form, in interaction with a component of a blow-off valve, a variable throttle point, with the higher working piston speeds a progressive Dämpfkraftverlauf can be achieved at increasing working piston speeds.
  • a progressive Dämpfkraftverlauf can be achieved at increasing working piston speeds.
  • additional components such as spool for forming this variable throttle point, can therefore be omitted, which leads to a structurally simple construction of the valve device and thus also to low manufacturing costs.
  • a small axial height of the valve device is achieved.
  • Fig. 1 the damping force curve of a vibration damper according to the invention is plotted against the working piston speed.
  • the region of the damping force profile labeled "region 1" is the region that is present during normal operation of the vibration damper at working piston speeds of up to about 2 m / sec. In this area, the damping force of the vibration damper by one or more resilient or spring-loaded valve discs certainly. If the working piston speed continues to increase, the damping force curve proceeds in a desired manner into a progressively increasing damping force profile.
  • "Gradually increasing damping force curve” means that with increasing piston speeds the damping force of the shock absorber also increases, thus reducing the damper speed before reaching the end stops to reduce the impact forces and avoid the damage and / or unwanted noise ,
  • the valve device unfolds its blow-off function, so that the progressively rising curve of the damping force curve merges into the flat region 2, in which there is no appreciable increase in the damping force. In this way, the formation of a too high pressure level is avoided within the vibration damper, so that a bursting of the vibration damper is prevented. At the same time, a high damping force level of the vibration damper is maintained.
  • Fig. 2a the functional principle of the valve device according to the invention is shown schematically during normal operation.
  • the working piston 1 which is arranged in an oscillating movable guided in a container tube 2 of a vibration damper.
  • the working piston 1 is acted upon by a valve disk 3 loaded with a spring force F2 spring , which cooperates with a valve seat formed on the body of the working piston 1.
  • This spring-loaded valve disc 3 forms in the in Fig. 2a illustrated compression stroke of the damper in the compression stage effective damping valve.
  • a spring- loaded by a second spring force F1 pressure relief valve 4 is shown, which also cooperates with a valve seat surface on the body of the working piston 1 and in Fig. 2a is shown in the closed state.
  • a variable throttle point 5 formed by the im in Fig. 2 illustrated normal operating state, the liquid damping medium flows through.
  • the damping force of the vibration damper changes.
  • the valve disc 3 only opens when the pressure in the vibration damper is so great that the force acting on the valve disc 3 by the damping medium is greater than the spring force F2 acting on the valve disc by the spring F2 spring .
  • the valve disc 3 then flows through the liquid damping medium, the flow channel 6 of the working piston and the adjoining variable throttle point 5, which is formed between the valve disc 3 and the pressure relief valve 4.
  • the pressure in the vibration damper also continues to rise, whereby the valve disk 3 is moved further against its spring force towards the blow-off valve 4 and the free, flow-through cross-sectional area of the throttle point 5 is further reduced.
  • the damping force of the vibration damper increases with increasing reduction of the free-flow cross-sectional area of the throttle point 5, so that the desired progressive Dämpfkraftverlauf is achieved.
  • a working piston 1 equipped with a valve device according to the invention is shown, which is arranged on a reduced diameter piston rod pin 7 of a piston rod 8.
  • the working piston 1 is tightened in a known manner with a nut 9 on the piston rod pin 7.
  • the working piston 1 has a flow channel 6 for the liquid damping medium.
  • the flow channel 6 can be covered by a valve disc 3 which cooperates with a valve seat 10 formed on the body of the working piston 1.
  • This valve disc 3 determines in the in Fig. 3 illustrated normal operating state, the damping force of the working piston in the compression stage.
  • the valve disc 3 is supported in a known manner by a spring disc package, which is supported in the axial direction up to the piston rod out at the radial shoulder of the piston rod.
  • valve disc 3 is preloaded with a predeterminable spring force, so that the valve disc 3 lifts off from the valve seat 10 only when a certain pressure is reached and releases a flow channel for the liquid damping medium.
  • Fig. 3 an arrow indicating the flow path of the damping medium during a compression stroke during normal operation is shown.
  • valve disc 3 cooperates with an annular disc 11 of the blow-off valve 4.
  • the pressure relief valve 4 with the blow-off function (blow-off valve) is in the in the Fig. 3 illustrated embodiment formed by a plurality of components.
  • a jacket 12 is provided, which cooperates with the body of the working piston 1.
  • a circumferential sealing surface is formed, on which the shell 12 of the blow-off valve 4 sealingly touches.
  • a radially inwardly extending paragraph 13 is provided on the inner wall of the shell 12.
  • the annular disc 11 is supported via a spacer ring 14 in the axial direction.
  • the course of the progressive increase of the damping force of the vibration damper can be influenced, since the distance between the valve disc 3 facing surface of the annular disk 11 can be predetermined by the valve disc 3 in the closed state via the spacer ring 14.
  • the jacket 12 of the blow-off valve 4 is held by a spring force generated by a spring washer 15 on the working piston 1 under bias.
  • This spring force corresponds to the in Fig. 2a, 2b with spring designated spring force.
  • the spring washer 15 is fixed axially fixed at its inner radial circumference in the region of the piston rod pin 7, while it rests on its outer periphery on two superimposed spacers 16, 17.
  • the support point, the spring washer 15 on the outer circumference is closer to the piston rod 8 as the point at which the spring washer 15 is held fixed in the region of the piston rod pin 7.
  • the spring washer 15 is bent so that it acts in the closing direction of the blow-off valve 4 spring force on the spacers 17, 16, the washer 11 and the spacer ring 14 on the Coat 12 exercises.
  • This bias holds the blow-off valve 4 in a closed position on the corresponding valve seat of the working piston 1. Only when a certain, dependent on the deflection of this spring washer 15 pressure in the vibration damper is reached, the blow-off valve 4 opens against the spring force of the spring washer 15 and gives the in Fig. 4 with an arrow shown flow path for the liquid damping medium free.
  • Fig. 4 a maximum deflection of the valve disc 3 is shown, in which the throttle body 5 (see. Fig. 3 ) is reduced to zero.
  • a critical level in which the free flow cross-section of the throttle point 5 (see Fig. 3 ) has reached such a low level that the throttle effect of the throttle point 5 is so great that in the vibration damper, a critical pressure is reached at which the blow-off valve 4 opens. This can also be the case even before the physical concern of the valve disc 3 on the annular disc 11. In order to achieve the opening pressure of the blow-off valve, it is therefore not necessary that the valve disc 3 rests against the annular disc 11.
  • the jacket 12 lifts off from its valve seat surface on the working piston 1 and releases a flow path for the liquid damping medium (blow-off function).
  • Fig. 5 the same operating principle of the valve device according to the invention is shown, as shown in Fig. 3 is shown using the example of a trained on the piston 1 valve device. The only difference is that in Fig. 5 a trained on a bottom valve 20 valve device according to the invention is shown. Same components are therefore in Fig. 5 denoted by the same reference numerals.
  • valve device At the in Fig. 5 shown normal operating state is also, as well as in Fig. 3 , The valve device according to the invention arranged so that it covers a flow channel 6, which is flowed through in a movement of the working piston 1 in the direction of the pressure chamber 30 of liquid damping medium (compression stroke).
  • the valve disc 3 is lifted against its biasing force to a certain extent from the valve seat 10, so that liquid damping medium flows through the channel 6 on the valve disc 3 and through the freely flow-through cross-section of the throttle body 5 therethrough.
  • the variable throttle body 5 is formed, is achieved by changing the desired progressive Dämpfkraftverlauf at high working piston speeds.
  • Fig. 6 is equipped with the valve device according to the invention bottom valve 20 according to Fig. 5 shown in a different operating state.
  • the valve disk 3 has deflected so far that the freely flow-through cross section of the throttle body 5 Fig. 5 ) has dropped to zero.
  • the pressure in the vibration damper has thereby increased to a critical level at which the jacket 12 of the blow-off valve 4 is lifted off the valve seat surface formed on the body of the base valve 20.
  • a flow path for the liquid damping medium is released, so that a further increase in the damping force is effectively avoided at even higher working piston speeds.
  • the damping force remains in a nearly constant manner at a certain high damping force level.
  • valve device according to the invention may be formed exclusively on the working piston 1 of the vibration damper, as shown in the Fig. 3 and 4 is shown. Equally, however, the valve device according to the invention can also be arranged exclusively on the bottom valve 20, as well as in the Fig. 5 and 6 is shown. Of course, it is also possible to provide the valve device according to the invention both on the working piston 1 and at the same time on the bottom valve 20.
  • valve device according to the invention is arranged in each case so that it is effective in the compression stage of the vibration damper.
  • the valve device according to the invention could also be arranged so that it is effective in the rebound of the vibration damper.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fluid-Damping Devices (AREA)
  • Safety Valves (AREA)
  • Fluid-Driven Valves (AREA)
  • Valve Device For Special Equipments (AREA)
  • Low-Molecular Organic Synthesis Reactions Using Catalysts (AREA)

Claims (12)

  1. Amortisseur de vibrations hydraulique
    a) avec un tube de chemisage (2), une tige de piston (8) en saillie dans le tube de chemisage (2) et pouvant être mue de manière oscillante dans celui-ci, à l'extrémité orientée vers le tube de chemisage (2) de laquelle est disposé un piston moteur (1), qui, présentant, pour le fluide amortisseur, des canaux de passage actifs dans la direction de traction et de pression, divise l'espace intérieur du tube de chemisage en un espace de traction (40), côté tige de piston, et en un espace de pression (30) éloigné de la tige de piston, au moins un premier canal de passage (6), pour la formation d'une valve d'amortissement, pouvant être recouvert avec un premier disque de valve (3), qui, faisant ressort ou étant soumis à un ressort, coopère avec un premier siège de valve (10),
    b) avec une valve de limitation de pression, avec une fonction de décharge (4) (valve "blow-off"), qui ouvre quand est atteint un premier niveau, qui peut être prédéterminé,
    c) et avec un premier point d'étranglement (5), qui génère une force d'amortissement évoluant progressivement avec la vitesse croissante du piston, et dont la section transversale d'étranglement varie en fonction de la vitesse du piston de l'amortisseur de vibrations, caractérisé en ce que
    d) la valve de limitation de pression (4) à fonction "blow-off" présente un premier disque annulaire (11), associé au premier disque de valve (3), avec une surface orientée vers le premier disque de valve (3), qui forme avec ledit premier disque de valve (3), le premier point d'étranglement variable (5),
    e) et en ce que la valve à fonction "blow-off" (4) présente une gaine cylindrique (12) avec un talon (13) radial, qui, disposé sur sa paroi interne et s'étendant vers l'intérieur, forme une butée pour le disque annulaire (11).
  2. Amortisseur de vibrations selon la revendication 1, au moins un canal de passage (6) pouvant être recouvert par le premier disque de valve (3), lequel canal est traversé par le fluide amortisseur lors d'un mouvement de plongée de la tige de piston (8) en direction de l'espace de pression (30).
  3. Amortisseur de vibrations selon revendication 1 ou 2, un plateau à valves (20), présentant, pour le fluide amortisseur, des canaux de passage (6) actifs dans la direction de traction et de pression, étant disposé à l'extrémité du tube de chemisage (2), située à l'opposé du côté de sortie de la tige de piston (8).
  4. Amortisseur de vibrations selon l'une des revendications précédentes, le premier disque de valve (3) et la valve "blow-off" (4) étant formés sur le piston moteur.
  5. Amortisseur de vibrations selon revendication 3 ou 4, le plateau à valves (20) présentant, pour la formation d'une valve d'amortissement, un deuxième disque de valve (3) et une valve "blow-off" (4), qui comprend un deuxième disque annulaire (11) et est associée à ce deuxième disque de valve (3), le deuxième disque de valve (3) formant, avec la surface du deuxième disque annulaire (11) orientée vers lui, un deuxième point d'étranglement (5), qui provoque un accroissement progressif de la force d'amortissement en fonction de l'accélération de la vitesse du piston.
  6. Amortisseur de vibrations selon la revendication 5, au moins un premier canal de passage (6), qui est traversé par le fluide d'amortissement, en direction de l'espace de pression (30), lors d'un mouvement de plongée de la tige de piston (8), pouvant être couvert par le deuxième disque de valve (3).
  7. Amortisseur de vibrations selon l'une des revendications précédentes, la valve "blow-off" (4) étant réalisée sous la forme d'une valve de limitation de pression soumise à un ressort.
  8. Amortisseur de vibrations selon l'une des revendications précédentes, une rondelle élastique (15) étant disposée à l'intérieur de la gaine (12) et au-dessus du talon (13), ladite rondelle élastique présentant un alésage central, et étant maintenue fixement dans la direction axiale dans la zone de cet alésage central, tandis que la rondelle élastique (15), sur son pourtour extérieur, s'appuie directement ou indirectement sur le talon (13), en développant une force élastique, qui agit dans la direction de fermeture de la valve "blow-off" (4).
  9. Amortisseur de vibrations selon la revendication 8, le disque annulaire (11), qui coopère avec le disque de valve (3), étant disposé entre le disque de valve (3) et la rondelle élastique (15).
  10. Amortisseur de vibrations selon la revendication 9, le disque annulaire (11) prenant appui sur le talon (13) de la gaine (12) par l'intermédiaire d'au moins une bague d'écartement (14).
  11. Amortisseur de vibrations selon la revendication 10, la rondelle élastique (15) prenant appui sur le disque annulaire (11) par l'intermédiaire d'au moins une bague d'écartement (16, 17), qui est disposée entre la rondelle élastique (15) et le disque annulaire (11).
  12. Amortisseur de vibrations selon l'une des revendications précédentes, la surface du siège de valve, avec laquelle la valve "blow-off" (4) coopère, étant formée sur le corps du piston moteur (1) et / ou sur le corps du plateau à valves (20).
EP06017716A 2005-09-27 2006-08-25 Dispositf de valve d'amortisseur ayant une évolution progressive de la force d'amortissement Active EP1767810B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102005046276A DE102005046276B3 (de) 2005-09-27 2005-09-27 Dämpfventileinrichtung mit progressivem Dämpfkraftverlauf

Publications (3)

Publication Number Publication Date
EP1767810A2 EP1767810A2 (fr) 2007-03-28
EP1767810A3 EP1767810A3 (fr) 2008-05-28
EP1767810B1 true EP1767810B1 (fr) 2010-03-10

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EP06017716A Active EP1767810B1 (fr) 2005-09-27 2006-08-25 Dispositf de valve d'amortisseur ayant une évolution progressive de la force d'amortissement

Country Status (5)

Country Link
US (1) US7584829B2 (fr)
EP (1) EP1767810B1 (fr)
AT (1) ATE460601T1 (fr)
DE (2) DE102005046276B3 (fr)
ES (1) ES2340410T3 (fr)

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US11859644B2 (en) 2020-03-24 2024-01-02 Stabilus Gmbh Piston assemblies and methods of using same
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CN113494610B (zh) * 2021-07-08 2023-06-27 西华大学 具有阻尼支撑的浮动环结构及机械密封装置
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CN100526674C (zh) * 2004-05-25 2009-08-12 日产自动车株式会社 液压缓冲器

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ES2340410T3 (es) 2010-06-02
US7584829B2 (en) 2009-09-08
EP1767810A3 (fr) 2008-05-28
EP1767810A2 (fr) 2007-03-28
DE502006006380D1 (de) 2010-04-22
US20070068753A1 (en) 2007-03-29
DE102005046276B3 (de) 2007-06-14
ATE460601T1 (de) 2010-03-15

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